US7520282B2

Undercarriage for automatic pool cleaner

Summary by NHIP

Pool cleaner with pivoting undercarriage

The automatic cleaner features a wheeled undercarriage with a pivotable second section that negotiates sharp corners between pool floors and walls. First and second axially spaced endless tracks extend about first, second, and third axles, while a turbine driven by liquid flow powers the first axle.

Claim Score by NHIP

Read claim 1, the broadest

Abstract

An automatic swimming pool cleaner includes a body (18) and a wheeled undercarriage (42) for the body. The undercarriage comprises a first submerged surface (14) engaging section (50) and a normally leading second section (52). The second section is pivotable in elevation (alpha) relative to the first section. The pivotable second section enables the cleaner to negotiate sharp corners between a floor (14) and a wall (16) of the pool and further lengths a wheelbase provided by the first section during reverse motion of the cleaner. A surface engaging brake (81) on the second section facilitates change of direction during reverse motion of the cleaner.

US7520282B2, drawing sheet 1 — Sheet 1 of 22

Term

Term ended

Expired 29 November 2023, 2.8 years ago.

11 claims: 1 independent, 10 dependent

1
Broadest claimClaim Score 33, narrow(NHIP)An automatic cleaner for surfaces submerged in a liquid, the surfaces including a substantially vertical wall of a pool, comprising:a body;a wheeled undercarriage for the body;the wheeled undercarriage comprising a first submerged surface engaging section and a second section;the second section being pivotable in elevation relative to the first submerged surface engaging section;wherein the first submerged engaging surface section extends between a first axle on the body and a second axle, wherein the second section extends between the second axle and a third axle, wherein the second axle and the third axle are mounted on a front assembly which is pivotable relative to the body in order to engage and climb the substantially vertical wall of the pool, wherein the first axle is coupled to a rear part of the body and wherein the front assembly is pivotably mounted on a front region of the cleaner, wherein first and second axially spaced endless tracks are provided to extend about the first axle, the second axle, and the third axle, wherein the first endless track extends about respective first wheels on the first, second and third axles and wherein the second endless track extends about respective axially spaced second wheels on the first, second and third axles, and wherein a surface engaging roller is provided on at least one of the first, second and third axles to extend between the first and second wheels on the at least one of the first, second and third axles wherein the first axle is driven by a turbine mounted in the body, and the turbine is driven by liquid flowing through the cleaner body under the influence from a remote suction pump which is connectable to the body in order to clean the pool by filtration.

71 paragraphs in 5 sections, as filed

TECHNICAL FIELD

THIS invention relates to automatic cleaners for surfaces submerged in a liquid and more particularly to such cleaners which are operated by a liquid driven turbine.

Known suction and pressure operated turbine driven cleaners for a floor and walls of a swimming pool suffer from the disadvantage that when they move through a sharp corner region between the floor and a wall, traction and suction are lost which impede their ability to scale the wall. Furthermore, operation of gear change mechanisms on the known machines for causing the cleaner to change from movement in a first direction to movement in an opposite direction is, due to the complex nature of these mechanisms, not reliable enough, which results in damage to gears and even jamming and malfunctioning of the mechanisms.

OBJECT OF THE INVENTION

Accordingly it is an object of the present invention to provide an alternative cleaner with which the applicant believes the aforementioned disadvantages may at least be alleviated.

DISCLOSURE OF THE INVENTION

According to the invention there is provided an automatic cleaner for surfaces submerged in a liquid comprising: <ul><li id="ul0001-0001" num="0000"><ul><li id="ul0002-0001" num="0005">a body;</li><li id="ul0002-0002" num="0006">a wheeled undercarriage for the body;</li><li id="ul0002-0003" num="0007">the undercarriage comprising a first submerged surface engaging section and a second section;</li><li id="ul0002-0004" num="0008">the second section being pivotable in elevation relative to the first section.</li></ul></li></ul>

The second section preferably leads the first section during normal forward motion of the cleaner.

The first section may extend between a first axle on the body and a second axle, the second section may extend between the second axle and a third axle and the second axle and third axle may be mounted on a front assembly which is pivotable relative to the body.

The first axle may be journaled to a rear part of the body and the front assembly may be pivotably mounted on a front region of the cleaner.

The front assembly may comprise first and second spaced arms between which the second and third axles extend.

First and second axially spaced endless tracks are preferably provided to extend about the first, second and third axles.

The first endless track preferably extends about respective first wheels on the first, second and third axles and the second endless track extends about respective axially spaced second wheels on the first, second and third axles.

A surface engaging roller may be provided on at least one of the first, second and third axles to extend between the first and second wheels on said at least one axle.

The first axle is preferably driven by a turbine mounted in the body. The turbine may be driven by liquid flowing under the influence of suction, alternatively pressure. Hence the turbine may be driven by liquid flowing through the cleaner body under the influence of a remote suction pump which is connectable to the body.

The turbine may be connectable to the first axle via a gear change mechanism to cause the axle to rotate in a selected one of a first direction to cause the cleaner to move in a forward direction and a second direction to cause the cleaner to move in another direction.

At least one of said tracks may have formations thereon to cooperate with formations on at least some of the wheels on the second and third axles, to drive the second and third axles.

The cleaner may comprise a clutch associated with one of the second and third axles for arresting the associated axle during reverse motion of the first axle, to enable the tracks to cause the front assembly to pivot from a first position to a second position.

When the front assembly is in the first position, the first section may provide a short wheelbase and when the assembly is in the second position, the first section may provide a longer wheelbase.

A surface engageable brake may be provided on one of the first and second arms of the front assembly and the assembly may cause the brake to engage a surface while the assembly is pivoting towards the second position.

The clutch may comprise a ratchet wheel mounted on the third axle and a cooperating pawl mounted on the body, the pawl allowing the wheel to rotate in a first direction.

The cleaner body may comprise a release mechanism for causing the pawl to release the ratchet wheel when the front assembly is in the second position.

The aforementioned turbine may comprise only three equi-spaced, curved vanes.

BRIEF DESCRIPTION OF THE ACCOMPANYING DIAGRAMS

The invention will now further be described, by way of example only, with reference to the accompanying diagrams wherein:

<figref idrefs="DRAWINGS">FIG. 1</figref> is a diagrammatic isometric view of an automatic pool cleaner according to the invention from the front, one side and above;

<figref idrefs="DRAWINGS">FIG. 2</figref> is a similar view of the cleaner from the front, the other side and above;

<figref idrefs="DRAWINGS">FIG. 3</figref> is a similar view of the cleaner from the rear, the other side and below;

<figref idrefs="DRAWINGS">FIG. 4</figref> is a view similar to <figref idrefs="DRAWINGS">FIG. 2</figref> with some parts of the cleaner broken away to show a water driven turbine for driving the cleaner;

<figref idrefs="DRAWINGS">FIG. 5</figref> is a diagrammatic representation of part of a drive mechanism including a rear driven axle of the cleaner;

<figref idrefs="DRAWINGS">FIG. 6</figref> is a more detailed diagrammatic representation of the part of the mechanism driving the rear axle;

<figref idrefs="DRAWINGS">FIG. 7</figref> is a diagrammatic three-dimensional view of a toggle mechanism of a gear change mechanism for the cleaner to cause a drive axle of the cleaner to change between motion in a first direction and motion in a reverse direction;

<figref idrefs="DRAWINGS">FIG. 8</figref> is a diagrammatic three-dimensional view of a cam arrangement for operating the toggle mechanism;

<figref idrefs="DRAWINGS">FIG. 9</figref> is a side view of the cam and toggle mechanisms with the toggle mechanism in a first position and about to be operated by the cam arrangement to move towards a second position;

<figref idrefs="DRAWINGS">FIG. 10</figref> is a view similar to <figref idrefs="DRAWINGS">FIG. 9</figref>, but with the toggle mechanism in the second position and about to be operated by the cam arrangement to move towards the first position;

<figref idrefs="DRAWINGS">FIG. 11</figref> is a diagrammatic side view of the cleaner from said other side and illustrating a pivotal section of a wheeled undercarriage of the cleaner in a normal position, but not showing endless tracks forming part of the undercarriage;

<figref idrefs="DRAWINGS">FIG. 12</figref> is a view similar to <figref idrefs="DRAWINGS">FIG. 11</figref> with the pivotal section moving towards a second position;

<figref idrefs="DRAWINGS">FIG. 13</figref> is a view similar to <figref idrefs="DRAWINGS">FIG. 11</figref> with the pivotal section in the second position;

<figref idrefs="DRAWINGS">FIG. 14</figref> is a diagrammatic side view of the cleaner approaching a corner region between a floor and a sidewall of a swimming pool;

<figref idrefs="DRAWINGS">FIG. 15</figref> is a view similar to <figref idrefs="DRAWINGS">FIG. 14</figref> with the cleaner negotiating the corner region;

<figref idrefs="DRAWINGS">FIG. 16</figref> is another view similar to <figref idrefs="DRAWINGS">FIG. 14</figref> with the cleaner starting to scale the side wall;

<figref idrefs="DRAWINGS">FIG. 17</figref> is a diagrammatic isometric view of the cleaner from the rear, the one side and above, illustrating a lid on the body in an open position, to expose the turbine;

<figref idrefs="DRAWINGS">FIG. 18</figref> is a diagrammatic isometric view of a second embodiment of a gear change mechanism for the cleaner with the gears in a configuration to drive a drive axle of the cleaner in a first or forward direction;

<figref idrefs="DRAWINGS">FIG. 19</figref> is a view similar to <figref idrefs="DRAWINGS">FIG. 18</figref> with the gears in a configuration to drive the axle in a second or reverse direction;

<figref idrefs="DRAWINGS">FIG. 20</figref> is a diagrammatic three dimensional view of a cam arrangement forming part of the gear change mechanism about to move the mechanism into the configuration shown in <figref idrefs="DRAWINGS">FIG. 19</figref>; and

<figref idrefs="DRAWINGS">FIG. 21</figref> is a view similar to <figref idrefs="DRAWINGS">FIG. 20</figref> with the cam arrangement about to move the gear arrangement into the configuration shown in <figref idrefs="DRAWINGS">FIG. 18</figref>.

DESCRIPTION OF A PREFERRED EMBODIMENT OF THE INVENTION

An automatic swimming pool cleaner according to the invention is generally designated by the reference numeral 10 in the diagrams. The cleaner is a turbine driven suction cleaner which in use, is connectable in known manner via a water intake (not shown) in a pool 12 (shown in <figref idrefs="DRAWINGS">FIGS. 14 to 16</figref>) to an inlet of an electrical circulation pump (not shown) of a circulation and filtration plant (also not shown) for the swimming pool 12.

The cleaner in use moves over a floor 14 and walls 16 of the pool and under the influence of the suction generated by the pump, sucks up water entraining debris and the like which is then filtered by the filtration plant, before the water is returned into the pool via suitably positioned outlets (not shown) into the pool.

The cleaner 10 comprises a body 18 defining a liquid flow passage 20 (shown in <figref idrefs="DRAWINGS">FIG. 4</figref>) therethrough. The flow passage 20 extends between an inlet 22 into the body 18 defined in a bottom plate 24 of the body and an outlet 26 from the body. A rotatable turbine 28 for driving the cleaner is mounted in a chamber 30 in the body to extend into the passage 20, to be driven by water moving under the influence of suction from the pool towards the pump. The turbine comprises three equi-spaced curved vanes 28.1 to 28.3. When driven, the turbine rotates in one direction namely a clockwise direction only, as shown in <figref idrefs="DRAWINGS">FIG. 4</figref>.

As shown in <figref idrefs="DRAWINGS">FIGS. 4 and 17</figref>, chamber 30 comprises a lid 32 which is mounted on body 18 at hinges 34, to pivot between a closed operative position shown in <figref idrefs="DRAWINGS">FIG. 4</figref> and an open position shown in <figref idrefs="DRAWINGS">FIG. 17</figref>. When in the open position, debris or the like may be removed from chamber 30. On the lid 32 there are provided dual in line ball joints 36 and 38 to enable spigot 40 defining outlet 26 to pivot relative to the body.

In use, the spigot 40 is removably receivable in a socket defined in a conventional flexible hose (not shown) which in use is used to connect the cleaner 10 to the aforementioned intake in the pool 12, as hereinbefore described.

The cleaner 10 comprises a wheeled undercarriage 42 for the body 18, best shown in <figref idrefs="DRAWINGS">FIG. 4</figref>. The undercarriage 42 comprises first, second and third parallel wheeled axles 44, 46 and 48. The first axle 44 is journaled to the body 18 as shown in <figref idrefs="DRAWINGS">FIGS. 1 and 2</figref>. The first axle 44 and second axle 46 provide a first section 50 (shown in <figref idrefs="DRAWINGS">FIG. 14</figref>) of the undercarriage. The second axle 46 and third axle 48 provide a second or front section 52 of the undercarriage and are mounted on an assembly 54 which is pivotable relative to a front end of the body, as shown in <figref idrefs="DRAWINGS">FIGS. 11 to 16</figref>. As shown in <figref idrefs="DRAWINGS">FIGS. 14 and 15</figref> with the first section 50 negotiating a surface 14, the second section 52 is pivotable in elevation (α) relative to the first section. The advantages and use of the pivotable section 52 will be described hereinafter.

As shown in <figref idrefs="DRAWINGS">FIGS. 1</figref>, 2, 4 and 11 to 16, the pivotable assembly 54 comprises opposed arms 80 and 82 which are pivoted at 84 and 86 to respective forwardly directed extension formations 88 and 90 from body 18. Axles 46 and 48 are journaled between the arms 80 and 82. A brake 81 comprising an elongate member 83 is pivotably mounted at 85 on arm 80. A guide 87 fast with formation 88 extends through an elongate slot 89 defined in the member 83. At its distal end, the brake comprises a formation 91 for engaging a surface of the pool as will hereinafter be described.

As shown in <figref idrefs="DRAWINGS">FIGS. 4 and 5</figref>, on axle 44 there are provided a first toothed wheel 60 and an opposed second toothed wheel 62. A first roller 64 is mounted to extend coaxially between the wheels. On the second axle 46 there are provided a first toothed wheel 66 and a second spaced wheel 68. A second roller 70 is mounted to extend coaxially between the first wheel 66 and second wheel 68. On the third axle 48 there are provided a first wheel 72 and spaced second toothed wheel 74. A third roller 76 extends between the first wheel 72 and second wheel 74.

As shown in <figref idrefs="DRAWINGS">FIGS. 2 and 3</figref>, a first endless track 92 extends about the first wheels 60, 66 and 72 on the axles 44, 46 and 48 and a transversely spaced second endless track 94 extends about the second wheels 62, 68 and 74 on the aforementioned axles. On inside surfaces of the tracks, there are provided formations 96 for cooperating with teeth 98 on the toothed wheels.

As best shown in <figref idrefs="DRAWINGS">FIGS. 2</figref>, 4, 5, 6 and 7 turbine 28 drives a hexagonal shaft 100 of stainless steel. A first bevel gear 102 is fast at an end of shaft 100 with its bevel facing the shaft. A second bevel gear 104 is also fast with the shaft, but spaced from the first gear and with its bevel facing towards the first gear. The shaft 100 is programmably moveable in an axial direction by a toggle mechanism 106 (shown in <figref idrefs="DRAWINGS">FIG. 2</figref>) relative to the turbine 28 between a first or normal position (shown in <figref idrefs="DRAWINGS">FIG. 3</figref>) wherein the first gear 102 engages a beveled driven gear 108 and a second position (shown in <figref idrefs="DRAWINGS">FIGS. 1 and 2</figref>) wherein the second bevel gear 104 engages the driven gear 108.

Gear 108 is fast with rotary drive shaft 110 journaled by bearings 109 on the body 18 and having a further bevel gear 112 fast at an opposite end thereof. The further bevel gear 112 meshes with a cooperating bevel gear 114 which is fast with hexagonal first axle 44.

As shown in <figref idrefs="DRAWINGS">FIG. 6</figref>, first wheel 60 which is fast with axle 44 comprises a plurality of radially extending spokes 116. The spokes 116 engage with cooperating slots 118 defined in cheek or end plate 120 which is fast with first roller 64. The second wheel 62 on the first axle 44 is similarly fast with axle 44 and a second cheek or end plate on the first roller adjacent the second wheel. The roller 70 is similarly fast with its adjacent wheels and axle. Roller 76 is similarly fast with the axle 48 and second wheel 74. The rollers are hollow and may house floats to provide suitable buoyancy in different parts of the cleaner.

Referring now to <figref idrefs="DRAWINGS">FIGS. 1</figref>, 2, 7 to 10, the toggle mechanism 106 comprises a generally inverted y-shaped member 120 pivoted to the body 18 at 122. The turbine driven shaft 100 is fast with a bush 124 defining a socket 126 through which the shaft 100 extends. As best shown in <figref idrefs="DRAWINGS">FIG. 7</figref>, the bush 124 is mounted in a bearing 125 allowing rotation of the bush and shaft 100. The bearing 125 in turn is mounted in a bearing holder 127 which is pivotable between legs 131 and 132 of member 120 and also slidable in a direction X as shown in <figref idrefs="DRAWINGS">FIG. 2</figref> by opposed stubs 135 on the holder which extend into opposed slots 133 defined in the legs 131 and 132.

As shown in <figref idrefs="DRAWINGS">FIG. 7</figref>, a foot part 130 of one leg 132 of the member 120 extends to a region between two spaced housings 134 and 136 on the body 18. In the housings 134 and 136 there are mounted magnets 138 and 140 respectively. A first pole of magnet 138 faces the foot and an opposite pole of magnet 140 also faces the foot. In the foot 130 there is also mounted a magnet 142 with its first pole facing a similar or like pole of magnet 138 and its opposite pole facing a similar pole of magnet 140.

The pivotal member 120 comprises an integral stub 144 defining a slot 146 between the stub 144 and an upper region of leg 132. A first lobe 150 of a passive cam 152 pivotably mounted on the body 18 at 154 extends into the slot 146. A second lobe 156 of the cam 152 cooperates with a driven cam 160. The driven cam 160 is mounted on the body 18 for rotation in an anti-clock wise direction A (shown in <figref idrefs="DRAWINGS">FIG. 7</figref>) about an axis 162. The cam may be driven by the turbine 28 alternatively and in a preferred embodiment the cam 160 is driven by a further turbine and reduction gear train housed in a box 164 shown in <figref idrefs="DRAWINGS">FIGS. 1 and 17</figref>. The further turbine is driven by water flowing through inlet 165 into the box and into the passage way 20 to the suction pump. The gear train linked with the further turbine drives square shaft 166 on which the cam 160 is mounted.

As shown in <figref idrefs="DRAWINGS">FIG. 8</figref>, the cam 160 comprises a first short lobe 168 cooperating with lobe 156 of passive cam 152 and a second longer lobe 170 cooperating with stub 144 in use.

It will be appreciated that with the like poles of magnets 138, 140 and 142 repelling one another, the pivotable member 120 has two stable positions. The first is an extended position shown in <figref idrefs="DRAWINGS">FIGS. 9 and 3</figref> wherein bevel gear 102 meshes with driven gear 108. With this arrangement the turbine drives the cleaner in a forward direction B, shown in <figref idrefs="DRAWINGS">FIG. 4</figref>. The second is a retracted position shown in <figref idrefs="DRAWINGS">FIGS. 1</figref>, 2, 7, 8 and 10 wherein the second bevel gear 104 meshes with driven gear 108. With this arrangement the turbine drives the axle 44 and cleaner in an opposite or reverse direction C, shown in <figref idrefs="DRAWINGS">FIG. 4</figref>.

Referring to <figref idrefs="DRAWINGS">FIG. 9</figref>, with the first bevel gear 102 engaging drive gear 108 and the pivotal member 120 in the extended position, shorter lobe 168 of cam 160 rotating in an anti-clockwise direction D engages second lobe 156 of passive cam 152. The passive cam is urged in a clockwise direction E as shown in <figref idrefs="DRAWINGS">FIG. 9</figref>. The longer lobe 150 of the passive cam engages stub 144 and urges the pivotal member 120 to pivot in an anti-clockwise direction. The lobe 168 engages the lobe 156 until after a critical point when the repelling forces of the magnets cause foot 130 and the member 120 to accelerate towards the second position shown in <figref idrefs="DRAWINGS">FIG. 10</figref> wherein the shaft is moved axially so that the second bevel gear 104 engages the driven gear 108 quickly and cleanly. As stated hereinbefore, the turbine 28 now drives the axle 44 in the reverse direction.

As shown in <figref idrefs="DRAWINGS">FIG. 10</figref>, the rotating cam 160 continues until the longer lobe 170 engages stub 144. This lobe urges the stub 144 and the member 120 to pivot in a clockwise direction F until beyond a critical point wherein the repelling forces of the magnets again cause the member to move quickly into the first or extended position shown in <figref idrefs="DRAWINGS">FIG. 9</figref> and wherein first bevel gear 102 again quickly and cleanly engages the driven gear 108.

The time periods during which the cleaner will move in the forward direction B and in the reverse direction C are programmable by suitable adjustment of the relative configuration of the lobes 168 and 170 of the rotating cam 160. It is believed that the sharp action caused by the repelling forces of the magnets will cause the relevant gear 102 and 104 smoothly and cleanly to engage the driven gear 108.

In other embodiments, the magnets may be replaced by suitable alternative biasing mechanisms or arrangements, such as arrangements comprising springs.

As best shown in <figref idrefs="DRAWINGS">FIGS. 1 and 11</figref> to 13 there is provided a ratchet wheel 180 on the third axle 48 between the first wheel 72 and third roller 76. A pawl 182 cooperating with the ratchet wheel is pivotably anchored at 184 on body 18. While the axle 44 moves in the clock-wise direction as shown in <figref idrefs="DRAWINGS">FIG. 11</figref>, the pawl simply slips over teeth on the ratchet wheel. However, when the axle 44 starts to move in the reverse direction to cause the cleaner to move in direction C, the pawl 182 engages the wheel 180, thereby to stop rotation of the third axle 48.

The opposed tracks 92 and 94 driven by the rear axle 44 now cause the second section 52 of the undercarriage to pivot in an anti-clockwise direction G as shown in <figref idrefs="DRAWINGS">FIGS. 12</figref> though 13. At the same time brake 81 is pivoted in the same direction and formation 91 engages the surface 14 as shown in <figref idrefs="DRAWINGS">FIG. 13</figref>. This causes the one side of the cleaner to move faster around brake 81 and the cleaner to change direction. Pawl 182 is released when it engages the formation 200 on the body 18, so that the cleaner is free to move in a reverse direction. The pivoting of section 52 during reversal of the machine automatically changes a relatively short wheelbase 186 (shown in <figref idrefs="DRAWINGS">FIG. 11</figref>) of first section 50 of the undercarriage during normal forward movement into a relatively longer wheelbase 188 (shown in <figref idrefs="DRAWINGS">FIG. 13</figref>), which improves the cleaner's stability when in reverse.

When the cleaner resumes normal forward motion as hereinbefore described, that is when bevel gear 102 engages driven gear 108, the pivotal section 52 of the undercarriage automatically pivots towards the normal position as shown in <figref idrefs="DRAWINGS">FIG. 14</figref> with the shorter wheelbase and wherein the brake 81 is lifted.

In other embodiments, a similar brake (not shown) may be provided in any other suitable position on the machine (for example adjacent each of wheels 60 and 62 at the rear of the machine) and which may intermittently be operated by the turbine 28 or the further turbine via cams or the like, to engage the surface 14, thereby to cause the machine intermittently to change direction. In a case where two brakes are provided as aforesaid, they may be operated alternatively.

In <figref idrefs="DRAWINGS">FIGS. 14</figref> through to 16 there is illustrated the cleaner 10 negotiating a corner region in the pool 12. In <figref idrefs="DRAWINGS">FIG. 14</figref>, the pivotable section 52 is in a normal position. As shown in <figref idrefs="DRAWINGS">FIG. 15</figref>, when the forwardly moving cleaner 10 engages the sidewall 16, the pivotable section 52 pivots in an anti-clockwise direction G better to conform to the profile of the corner region. Substantial parts of tracks 92 and 94 engage both the floor 14 and wall 16 to maintain traction. As shown in <figref idrefs="DRAWINGS">FIG. 16</figref>, as the cleaner moves closer to and up the wall, the pivotable section progressively pivots in direction H towards the normal position, thereby to maintain sufficient traction and/or suction while the cleaner moves through the corner region. Once on the wall 16, the cleaner continues its movement along the wall in the normal configuration as shown in <figref idrefs="DRAWINGS">FIG. 14</figref>, although there it is shown in normal configuration on the floor.

An alternative embodiment of the drive mechanism and gear change mechanism is shown in <figref idrefs="DRAWINGS">FIGS. 18 to 21</figref>. In this embodiment the shaft 100 is square in transverse cross-section and is stationary in an axial direction. A worm gear 202 is fast with shaft 100. A gear 204 cooperates with the worm gear 202 to drive a cam 206 (shown in <figref idrefs="DRAWINGS">FIGS. 20 and 21</figref>) similar to cam 160. Hence, the further turbine and gear train in box 164 are dispensed with. Shaft 100 is further fast with a drive gear 207. The first axle 44 is driven by a belt and pulley arrangement comprising a pulley 208 fast with axle 44, a belt 210 and a pulley 212. Pulley 212 is fast with a gear 214 of a pivotable assembly 215 also comprising a gear 216 on an extension arm 218.

The assembly 215 is pivotable between a first normal position shown in <figref idrefs="DRAWINGS">FIG. 18</figref> and a second position shown in <figref idrefs="DRAWINGS">FIG. 19</figref>. In the first position, the drive gear 207 drives gear 216 which in turn drives gear 214. Gear 214 drives the belt and pulley arrangement, so that the cleaner moves in a forward direction. In the second position shown in <figref idrefs="DRAWINGS">FIG. 19</figref>, the drive gear 207 drives gear 214 directly, so that the direction of rotation of axle 44 is reversed.

The assembly 215 is pivoted by the cam 206 which is similar to cam 160 hereinbefore described and cam 218 which is similar to cam 152 hereinbefore described. As shown in <figref idrefs="DRAWINGS">FIG. 20</figref>, lobe 220 of cam 206 urges the assembly in a clock-wise direction to bring gear 214 into direct meshing relationship with drive gear 207 thereby to reverse the direction of rotation of axle 44. As shown in <figref idrefs="DRAWINGS">FIG. 21</figref>, lobe 222 of cam 206 thereafter cooperates with lobe 224 of cam 218 to cause lobe 226 of cam 218 to pivot the assembly back towards its normal position wherein drive gear 207 meshes with intermediate gear 216 which in turn drives gear 214 as hereinbefore described. The assembly 215 is caused to move quickly to the first and second positions by a suitable toggle mechanism comprising magnets, similar to the mechanism hereinbefore described or other suitable biasing mechanisms.

Contents5

Every citation, both waysCites: the store holds 71 of 72

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US5256207A	Cites	United States of America	Applicant
US5337434A	Cites	United States of America	Applicant
US5412826A	Cites	United States of America	Applicant
US5435031A	Cites	United States of America	Applicant
US5443354A	Cites	United States of America	Applicant
US5507058A	Cites	United States of America	Applicant
US5539947A	Cites	United States of America	Applicant
US5542141A	Cites	United States of America	Applicant
US5617600A	Cites	United States of America	Applicant
US5720068A	Cites	United States of America	Applicant
US5771987A	Cites	United States of America	Applicant
US5893188A	Cites	United States of America	Applicant
US5933899A	Cites	United States of America	Applicant
US5976385A	Cites	United States of America	Applicant
US6003184A	Cites	United States of America	Applicant
US6039886A	Cites	United States of America	Applicant
US6061860A	Cites	United States of America	Applicant
US6094764A	Cites	United States of America	Applicant
US6115864A	Cites	United States of America	Applicant
US6131227A	Cites	United States of America	Applicant
US6132287A	Cites	United States of America	Applicant
US6206547B1	Cites	United States of America	Applicant
US6212725B1	Cites	United States of America	Applicant
US6237175B1	Cites	United States of America	Applicant
US6280611B1	Cites	United States of America	Applicant
US6292970B1	Cites	United States of America	Applicant
US6358425B1	Cites	United States of America	Applicant
US6387250B1	Cites	United States of America	Applicant
US6412133B1	Cites	United States of America	Applicant
US6560808B2	Cites	United States of America	Applicant
US6564417B2	Cites	United States of America	Applicant
US6581232B1	Cites	United States of America	Applicant
US6633150B1	Cites	United States of America	Applicant
US6665900B2	Cites	United States of America	Applicant
US6742613B2	Cites	United States of America	Applicant
US6758226B2	Cites	United States of America	Applicant
US6782578B1	Cites	United States of America	Applicant
US6820297B2	Cites	United States of America	Applicant
US6842931B2	Cites	United States of America	Applicant
US6854148B1	Cites	United States of America	Applicant
US6886205B1	Cites	United States of America	Applicant
ZA8904904A	Cites	South Africa	Applicant

Showing 100 of 102

16 members in 7 offices

This recordMember, by publication datePriority claim

Priority claims12

Priority claims
Document	Office	Kind	Date
200100046	South Africa	A	2001-07-03
200100046	South Africa	A	2001-07-03
200201669	South Africa	A	2002-02-28
200201669	South Africa	A	2002-02-28
0200107	South Africa	W	2002-06-27
0200107	South Africa	W	2002-06-27
010046	–	–	–
021669	–	–	–
PCTZA0200107	–	–	–
WO2002ZA00107	–	–	–
ZA20010000046	–	–	–
ZA20020001669	–	–	–

Members16

Family members, oldest first
Document	Office	Kind
WO03004799A1	World Intellectual Property Organization (WIPO)	A1	2003-01-16
WO03004800A1	World Intellectual Property Organization (WIPO)	A1	2003-01-16
EP1402134A1	European Patent Office (EPO)	A1	2004-03-31
EP1402135A1	European Patent Office (EPO)	A1	2004-03-31
ZA200301775B	South Africa	B	2004-09-29
ZA200301776B	South Africa	B	2004-09-29
US2004211450A1	United States of America	A1	2004-10-28
US2004231075A1	United States of America	A1	2004-11-25
AU2002317622B2	Australia	B2	2008-01-10
AU2002319834B2	Australia	B2	2008-01-31
US7464429B2	United States of America	B2	2008-12-16
US7520282B2This record	United States of America	B2	2009-04-21
EP1402135B1	European Patent Office (EPO)	B1	2009-12-16
AT452260T	Austria	T	2010-01-15
ATE452260T1	Austria	T1	2010-01-15
DE60234768D1	Germany	D1	2010-01-28

52 transactions on the USPTO file

Allowed after 1 non-final rejection, 1 final rejection and 1 RCE.

Non-final rejections: 1
Final rejections: 1
RCEs: 1
Appeals: 0

Over time

Point at a mark for the transaction

Transactions

Prosecution transactions, newest first
	Event	Code
2013-05-17	Expire PatentEXP.	EXP.
2009-04-21	Recordation of Patent Grant MailedPGM/	PGM/
2009-04-21	Patent Issue Date Used in PTA CalculationAllowedPTAC	PTAC
2009-04-01	Issue Notification MailedAllowedWPIR	WPIR
2009-03-12	Dispatch to FDCD1935	D1935
2009-03-11	Application Is Considered Ready for IssuePILS	PILS
2009-03-10	Issue Fee Payment VerifiedN084	N084
2009-03-10	Issue Fee Payment ReceivedIFEE	IFEE
2008-12-10	Mail Examiner's AmendmentMEX.A	MEX.A
2008-12-10	Mail Notice of AllowanceAllowedMN/=.	MN/=.
2008-12-05	Notice of Allowance Data Verification CompletedAllowedN/=.	N/=.
2008-12-05	Case Docketed to Examiner in GAUDOCK	DOCK
2008-12-05	Examiner's Amendment CommunicationEX.A	EX.A
2008-09-26	Date Forwarded to ExaminerFWDX	FWDX
2008-09-26	Date Forwarded to ExaminerFWDX	FWDX
2008-09-26	Disposal for a RCE / CPA / R129AbandonedABN9	ABN9
2008-09-25	Request for Continued Examination (RCE)RCEX	RCEX
2008-09-25	Request for Extension of Time - GrantedXT/G	XT/G
2008-09-25	Workflow - Request for RCE - BeginBRCE	BRCE
2008-08-19	Change in Power of Attorney (May Include Associate POA)PA..	PA..
2008-08-13	Correspondence Address ChangeC.AD	C.AD
2008-03-25	Mail Final Rejection (PTOL - 326)Final rejectionMCTFR	MCTFR
2008-03-17	Final RejectionFinal rejectionCTFR	CTFR
2008-01-04	Date Forwarded to ExaminerFWDX	FWDX
2007-12-14	Response after Non-Final ActionA...	A...
2007-12-14	Request for Extension of Time - GrantedXT/G	XT/G
2007-10-04	Case Docketed to Examiner in GAUDOCK	DOCK
2007-07-27	Case Docketed to Examiner in GAUDOCK	DOCK
2007-07-02	Mail Non-Final RejectionNon-final rejectionMCTNF	MCTNF
2007-06-25	Non-Final RejectionNon-final rejectionCTNF	CTNF
2005-09-12	Information Disclosure Statement consideredIDSC	IDSC
2005-09-12	Reference capture on IDSRCAP	RCAP
2005-09-12	Information Disclosure Statement (IDS) FiledM844	M844
2005-09-12	Information Disclosure Statement (IDS) FiledWIDS	WIDS
2005-01-24	Case Docketed to Examiner in GAUDOCK	DOCK
2004-10-04	Preliminary AmendmentA.PE	A.PE
2004-09-28	Mail Non-Compliant Preliminary AmendmentMNPRL	MNPRL
2004-09-24	IFW TSS Processing by Tech Center CompleteTSSCOMP	TSSCOMP
2004-09-24	Non-Compliant Preliminary AmendmentNPRL	NPRL
2004-09-24	Case Docketed to Examiner in GAUDOCK	DOCK
2004-07-18	Cleared by OIPE CSRL194	L194
2004-07-06	Application Dispatched from OIPEOIPE	OIPE
2004-07-06	Notice of DO/EO Acceptance MailedM903	M903
2004-06-16	371 Completion Date371COMP	371COMP
2004-06-16	Additional Application Filing FeesADDFLFEE	ADDFLFEE
2004-06-16	A statement by one or more inventors satisfying the requirement under 35 USC 115, Oath of the ApplicOATHDECL	OATHDECL
2004-05-28	Notice of DO/EO Missing Requirements MailedM905	M905
2004-01-02	Information Disclosure Statement consideredIDSC	IDSC
2004-01-02	Information Disclosure Statement (IDS) FiledWIDS	WIDS
2004-01-02	Preliminary AmendmentA.PE	A.PE
2004-01-02	Request for Foreign Priority (Priority Papers May Be Included)RQPR	RQPR
2004-01-02	Initial Exam Team nnIEXX	IEXX

6 legal events, as the office reported them to INPADOC

Over the term

Point at a mark for the event

Events

Legal events, newest first
	Event	Code
2013-06-11	Lapsed due to failure to pay maintenance feeLapsedFP	FP
2013-05-20	Information on status: patent discontinuationPATENT EXPIRED DUE TO NONPAYMENT OF MAINTENANCE FEES UNDER 37 CFR 1.362STCH	STCH
2013-05-17	Information on status: patent discontinuationPATENT EXPIRED DUE TO NONPAYMENT OF MAINTENANCE FEES UNDER 37 CFR 1.362STCH	STCH
2013-04-21	Lapse for failure to pay maintenance feesLapsedLAPS	LAPS
2012-12-03	Maintenance fee reminder mailedREMI	REMI
2004-04-06	AssignmentAS	AS